Linkage connection for indicators



Nov. 8, 1960 w. F. BERCK LINKAGE CONNECTION FOR INDICATORS Original Filed July 30, 1956 INVENTOR. Zd/u/AM E 5:76!

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lrraINi/i Nov. 8, 1960 W. F. BERCK LINKAGE CONNECTION FOR INDICATORS Original Filed July 30, 1956 6 Sheets-Sheet 2 INVENTOR. U/LL/AM 5 510a:

BY WM Nov. 8, 1960 w. F. BERCK LINKAGE CONNECTION FOR INDICATORS Original Filed July so, 1956 6 Sheets-Sheet 3 INVENTOR. (Mu/4M A 5am:

Nov. 8, 1960 w. F. BERCK 2,959,058

LINKAGE CONNECTION FOR INDICATORS Original Filed July 30, 1956 6 Sheets-Sheet 4 I INVENTOR. MM/4M 1 75mm! Nov. 8, 1960 w. F. BERCK LINKAGE CONNECTION FOR INDICATORS 6 Sheets-Sheet 5 Original Filed July 30, 1956 \h M a a if u MIN 5 X4 6 m IIHI H u .HI 6 I o w L 7m INVENTOR. (dun/4M I? 5!!!! Nov. 8, 1960 W. F. BERCK LINKAGE CONNECTION FOR INDICATORS Original Filed July 30, 1956 6 Sheets-Sheet 6 ,erraem'fi LINKAGE CONNECTION FOR INDICATORS William F. Berck, Hayward, Calif., assignor to Ralph N. Brodie Company, San Leandro, Califi, a corporation of California 7 Claims. (Cl. 74-1) My invention relates to a linkage connection for indicators, and, more specifically, to an automatic temperature compensator for use in the measuring of flow of liquids. This application is a divisional application of my co-pending application Serial No. 600,888, filed July 30, 1956.

It is an object of my invention to provide an automatic temperature compensator for use with a liquid meter whereby the flow volume measured by the meter is automatically compensated for variations in the temperature of the liquid being metered.

A further object of the invention is to provide a temperature responsive actuator for use in an automatic temperature compensator which is unaffected by changes in ambient temperature and which is capable of produc ing a movement proportional to movement produced by a temperature sensitive means responsive to the temperature of the liquid being metered.

A further object of my invention is to provide a tem-' perature responsive actuator for use in an automatic temperature compensator wherein, by suitable linkage, the actuator is unaffected by change in ambient tempera ture, and wherein the actuator produces a movement proportional to movement produced by a temperature sensitive means responsive to the temperature of the liquid being metered, and whereby the proportionality of such movement may be adjusted to compensate for variations in the coefficient of expansion of the liquids being metered.

Other objects and advantages will become apparent in the detailed description to be hereinafter discussed.

bought and sold, except at the retail level, on a basic tes atentO 2,959,058 Patented Nov. 8, 1960 volume of a liquid, it is quite usual to discard the group number system and use coefficients of expansion which have been computed to the fifth decimal place.

It has long been recognized that the vast number of computations required from day to day to provide the 60 corrected volume of petroleum products transfers results in great cost as well as in numerous errors. It is highly desirable to secure these results automatically.

1 have invented an improved automatic temperature compensator for use with a positive displacement fluid meter whereby the volume indicator of the fluid meter is connected to the compensator and an automatic compensation is provided so that the output of the compensa: tor will be adjusted automatically to correct to a 60 volume. The compensator is also capable of being adjusted for different degrees of coefficients of expansion so that when so adjusted for a particular fluid a corrected volume indication will be automatically obtained even though the temperature of the fluid being metered may fluctuate through wide temperature differences.

In the accompanying drawings, forming a part of this application, and in which like numerals are employed to designate like parts throughout the same,

Fig. 1 shows a plan view, with parts broken away, of a preferred embodiment of my invention. 1

Fig. 2 is an elevational sectional view of the same, taken along line 22 of Fig. 1.

Fig. 3 is a partial elevational view of the same, taken along line 3--3 of Fig. 2.

Fig. 4 is a perspective view of the temperature responsive actuator.

Fig. 5 is an exploded view showing the arrangement of parts in the temperature responsive actuator.

Figs. 6 through 9 illustrate the relative position of the temperature responsive actuator for different conditions.

In terms of broad inclusion, the temperature compensator comprises an infinitely variable transmission in which the ratio of drive from input to output is varied proportionally to changes in the temperature of the liquid being metered, the degree of proportionality being capable of adjustment to compensate for the particular coefficient of expansion of the liquid being metered.

The changes in temperature of the metered liquid are automatically sensed by a thermostatic bulb, immersed in the liquid. The expansion of the liquid in the bulb temperature of 60 F., with the'transfer of such products being commonly on a volume basis. However, most of the transfers of such products are made at temperatures other than 60 with the result that the volume of the products must becorrected to the accepted 60 tempera-' Group I .0004 Group II .0005 Group III .0006 Group IV .0007 Group V .0008 Group VI .00085 Group VII .0009 Etc.

; However, .to determine more accurately the corrected is utilized to move a primary bellows, this movement,

in turn, being transferred through an appropriate linkage to an infinitely variable friction member which changes the ratio of the transmission drive in accordance with the coefficient of expansion of the liquid being metered.

Ambient temperatures, which might result in error, are automatically cancelled by a secondary bellows responsive only to atmospheric temperature.

In greater detail, reference numeral 10 generally indicates a housing having formed therethrough at the bottom and top side thereof axially aligned bores 11 and 12,

respectively. An input shaft 13 is mounted for rotation in anti-friction bearing 14 secured in bore 11. A coupling shaft 15 enables the input shaft 13 to be coupled to the volume indicator output shaft of a positive displacement liquid meter, of a type as illustrated in my prior patent, US. Patent No. 2,531,603.

Fixed to input shaft 13 is a drive gear 16, having twenty-two teeth, in meshing engagement with gear 17, having forty teeth. Gear 18, having twenty teeth, is

' compounded to gear 17 and fixed to shaft 19, journaled for free rotation in housing 10. Gear 18 is in meshing engagement with gear 21, having forty teeth, mounted for rotation around the output shaft 22. Gear 21 also serves as the hub and planet arm fora planetary system in which planet gears 23 and 24, mounted on shafts 26 and 27, respectively, carried by planet arm 28, mesh with the inner teeth 29 of ring g ar 30, having fortyeight inner teeth, to drive the output sun gear 32, having sixteen teeth. The sun gear 32 is journaled for rotation in anti-friction bearing33 mounted in bore 12 of housing 10, and fixed to output shaft 22. An output coupling 34 enables the output shaft to be connected to a conventional counting, or indicating, mechanism (not shown), whereby the number of revolutions of the output shaft may be recorded.

In a planetary system of the type described, the ratio of drive with the planet arm driving and the sun gear driven is expressed as R-l-S.

in which R- -=nu mber of inner teeth of the ring gear 30, and and S=numberof teeth of the output Sun gear. The overall drive ratio from input to output of the compound gear train described is thus equal to gear 16 gear 18 R+S gear 17 gear 21 Substituting the known number of teeth in each gear, we have or, for each revolution of the input shaft 13, the output shaft turns through 1.1 revolutions.

Compounded to gear 16, and thus driven by the input shaft 13, is a second gear 36, having forty teeth, in meshing engagement with a platform gear 37, having forty teeth, 'jou'rn aled for rotation in anti-friction bearing 38 mounted in housing 10.

A friction roller 39, having a spline 41a, is mounted on shaft 41, with the spline 41a slidably received within a longitudinal groove 41b formed in the shaft 41, thus allowing the friction roller 39 to move longitudnally along the shaft while coupling the roller and shaft against relative rotation. The shaft 41 is disposed above; the platform gear 37 so that the projected axis of 'the platform gear passes through the center of shaft 41; The friction roller has a circular friction surface 43 held in contact with the upper surface 44 of the platform gear 37, the friction, surface 43 being'formed with a /s inc-h outside diameter. Therefore,'when the friction surface 43 is bearing on the platform gear at, a radial distance of @4 inch from the center of the platform gear, the ratio of drive from the platform gear to the friction roller is onetoone. i

The friction roller shaft 4 1 is journaled'in anti-friction, bearing 46' mounted within slots 47, formedinstanchionsj 48 and 49. The slots-47 prevent horizontalmdv' of the bearing 46 while allowing vertical movem nt'of the bearing'in the slots. Aretaiiner plate 51, ver "lly slidably mounted on studs 52 and 53 fdrm'ed onthe uppei ends of stanchions 48 and '49, engages the uppefsurface 'of bearing 46, While spring 54 urges the 'p1a'te' 51do'wnwardly to force the friction surface 43 of the'frictio'rl roller 39 into engagement with the upper surface '44 of the platform gear 37. The other end of the 'shaft 41, i8; 6P3

mounted'in a similar manner, with retainer pla urged downwardly by spring/57.

A roller positioning slide 53 is slidably mounted above the retainer plates 51 and 56, with a stud 59Yon there; tainer plate 51 passing through a longitudinal "slot 61'. A downwardly directed stud 62 mounted on slide 58, fits Within a groove 63 found in the friction wheel 39, and an upward'y directed stud 64 in actuating lever 65.

passes through opening 654 It is thus seen that if the actuating arm is movedv in a horizontal direction, that the stud 62' will cause the friction roller .39 to move axially thereof-along shaft 41 in a direction radially of the platform gear Q7, with,

a change of 12% (1.06.94) in ratio between 4 rotation of the platform gear being transferred to the friction roller .and shaft 41.

Mounted on one end of the shaft 41 is a worm 66, having two teeth, in meshing engagement with Worm wheel 67, having sixteen teeth, fixed to shaft 68, journaled to housing 10. Gear 69, having sixteen teeth, is also fixed to shaft 8, and is in driving engagement with the outer teeth 71 of ring gear 30, the ring gear having sixty outer teeth. The ring gear 30 is driven by the last described cQm-Pound gear train in the same rotational direction as the sun gear 32.

Thus, presuming the planet arm 28 stationary, the input to ring gear 30 drive ratio of the last compound gear train described is equal to:

gear 36 platform gear setting gear 37 friction roller radius worm 66 gear 69 Worm gvheel ring gear 30 Substituting the number of teeth of each gear and assuming the friction roller to be inch from the center of the platform gear 37, the drive ratio is:

or, each revolution of the ring gear equals three revolutions, oftthe. sun gear.

' The friction roller 39 is designed to be moved radially of the platform gear with a minimum distance or plat-t form. setting of inch from the center thereof, and a maximum distance of inch from the center thereof, with a'rnean distance of inch. With these platform settings, 'we'may, now determine the total effect of one revolution of the input shaft 13 to the output shaft 22 at the various. platform settings, always presuming planet rq e tj aa t Combining these, ratios, with, the ratio originally. establishedas' nb'rinarto this planetary "system, or 1.1 revolutions of output for one revolution of input, We have as a total ratio I of input to output:

At min m m. p tformtsettingz. 1.1-04:166- At mean platform setting: 1.1..10=1.00 At m mumplatform, setting: 1.1V .16=.94

Thus, itis seen that with an eight-sixteenths of an incho'f adjustment in the relation of the friction roller,

39- to the center of the platform gear 37, there results shaft 13 and the output shaft 22.

Retempemture. c, 2111peusator. design istbased. one

the input.

3 fnean platform setting inch) at 60 F., for it is at this setting that a ratio from input to output is one to one. The variable speed transmission thus described provides for a 6% of change in this ratio due to temperature below 60 F. and for 6% of change in this ratio due to temperature above 60 F.

The heat responsive means comprises a liquid filled bulb 72 placed in close juxtaposition with the liquid stream being metered, a capillary tube 73, connecting this bulb with a liquid filled bellows '74-having a stem 76 to provide a definite axial movement for each degree of temperature change in the liquid stream. This type of thermal responsive bulb and bellows assembly is well known and designed so that the expansion of the liquid in the bulb and bellows produces a usable movement and force. The particular configuration of the bulb, capillary tube and bellows and the particular type of fluid used to fill the bulb and bellows have no bearing on this invention, it being essential only that movement of the stem 76 per degree of temperature change of the fluid being metered be a designated amount suitable to the mechanism. In the device disclosed, one degree of temperature change in the liquid being metered results in .00125 of an inch movement in stem 76.

The bulb 72, being in close contact with the stream of liquid, accurately assumes the temperature of that stream and the liquid contained within the bulb expands at a predetermined rate at a rise in temperature and conversely contracts with a fall in temperature. The capillary tube 73, providing communication between the bulb and bellows, has a very fine diameter, and thus the amount of fluid contained in the tube is of no practical significance. The bellows, however, contains an appreciable quantity of fluid and since this bellows is subject to ambient temperatures, the liquid contained therein will expand and contract in relation to changes in the ambient temperature rather than to the changes in the liquid temperatures. The influence of ambient temperatures in this system results in an erroneous movement of stem 76 which must be corrected.

Bellows 77 is so made that its response to ambient temperatures exactly matches the response of bellows 74 to ambient temperatures. A linkage, described hereinafter, acts in a manner to cancel out the movement of bellows 74 and 77 in response to ambient temperature changes so that the position of friction roller 39 on platform gear 37 is affected solely by the temperature changes in the liquid stream as sensed by bulb 72.

1 Stem 76 bears against lever 78 at 79, causing lever 78 to pivot about stud 81 mounted on frame 80, the frame 80 being fixed to housing 10. Stem 82 bears against a similar lever 83 at 84, causing lever 83 to pivot about stud 86 mounted on frame 80.

If both bellows 74 and 77 are expanding due to rising ambient temperatures, lever 78 will becaused to rotate in a' clockwise direction while lever 83 will be caused to rotate in a counterclockwise direction.

{Levers 78 and 83, opposite pivot points 81 and 86, have slots 87 and88'formed therethrough, respectively. A quadrilateral linkage or togglesystem 90, having four equal length toggle links 91, 92, 93 and 94 pivotally connected to each other at each corner of the toggle system, has a pivot stud 89 pivotally connecting links 91 and 92 at one corner of the toggle system 90, and riding within slot 87 of lever 78, and a second pivot stud 96 pivotally connecting links 93 and 94 at the opposite corner of the toggle system. 90, and riding within slot 88 of lever 83.

. Cross link 97 incorporates slots 98 and 99 which cooperate with studs 89 and 96; cross link 97 also being provided with a stud 101 which rides in slot 102 of slide link 103. At one end slide link 103 is fixed by means of hole 104 to pivot stud 106 of toggle system 90; at the opposite end of slide link 103 a slot 107 guides the pivot stud 8 inthe togglesystem, all these parts cooperating in such a manner that-slide link 103 and studs 106 and 108 are always positioned along a line which is at right angles to a line passing through the center of studs 81 and 86. The cross link 97 and slide link 103 constitute a means to pivotally move actuating lever 65 in response to movement of studs 106 and 108, which studs are operated by levers 78 and 83.

A carrier bracket 109 has fixed to itself two studs 111 and 112 which slidably position cross link 97 in a parand relationship to a line passing through pivot points 81 and 86 so that studs 89 and 96 are maintained at an equal distance from pivots 81 and 86, respectively.

Ina toggle system such as 90, in which each link is free topivot, ifstud 89 and stud 96 are moved toward each other at an equal rate and an equal distance, the lateral relationship of studs 106 and 108 will be undisturbed but the distance between studs 106 and 108' will be lengthened. Thus, it will be seen that, if due to the eflects of ambient temperature change bellows stem 76 and bellows stem 82 move the same distance at the same rate, levers 78'and 83 will rotate at an equal rate clockwise and counterclockwise, respectively, while studs 89 and 96, being positioned by cross slide 97 and carrier 109 at an equal distance from pivots 81 and 86, will move at an equalrate. Studs 106 and 108, being guided by slide link7103 and stud 101, will be undisturbed laterally but will move into a closer or farther relationship with each other along a line described by hole 104, slot 102 and slot 107, depending upon whether stems 76 and 82 are moving under the influence of a rising or a lowering temperature.

As described, under the influence of an ambient temperature change in bellows 74 and 77, the system of cooperating levers, links and toggles exactly absorbs this change without disturbing the lateral relationship of slide link 103 or toggle pivots 106 and 108.

Expansion of liquid in bulb 72 superimposes a movement of bellows 7 4 over and above any movement of this bellows caused by ambient temperature change so that position of bellows stem 76 is aflected not only by the ambient temperature of bellows 74 but also by the temperature of the liquid stream which has created a temperature change in bulb 72 substantially difierent from ambient temperature.

This additional movement of stem 76 is not compensated for by a similar movement of stem 82; therefore, stud 96 of toggle system 90 remains stationary. This movement of stem 76 causes lever 78 to pivot about stud 81, moving stud 89 in a direct relationship. With stud 96 stationary, movement of stud 89 then causes studs 106, 108, slide link 103 and slot 102, stud 101, cross link 97 and stud 113 to be displaced laterally.

In a toggle system such as described, in which all four links are of equal length, if pivot 96 is held stationary and if pivot 89 is moved either toward pivot 96 or away from that point, then studs 106 and 108 will move exactly one half of that amount. To explain this, suppose toggle links 93 and 92 were two equal sides of an isosceles triangle with line 8996 as a base. A perpendicular constructed to this base from apex 108 divides the base exactly in half; therefore, any increment of change in the length of line 89-96 will be reflected in just half that increment of movement on point 108 as well as point 106, slide link 103, cross link 97 and stud 113.

Stud 113 extends into slot 114 of lever 65, which is pivoted at 116 on fixed stud 117 mounted on base and at its opposite end has a hole 65a which cooperates with stud 62 of roller positioning slide 58. Stud 62 in slide 58 riding in groove 63 of roller 39 causes the 4 roller torbe positioned in response to movement of slide 58 and lever 65.

'Therefore, expansion or contraction of liquid in bellows 72 due to changes in temperature of a liquid stream superimposes a movement of bellows 74 and stem 76 other than that causedby. ambient temperature and through the linkage described causes a movement of roller 39 on platform gear 37 which changes the ratio of drive between these points and, through an appropriate planetary gear system, causes a change of ratio between input 13 and output 22 of the temperature compensatgor.

In a device of this nature, composed of various levers, links and joints, looseness or backlash could interfere seriously with accurate response. To insure accuracy of response as initiated by bellows 74 and 77, a tension spring 118 is attached to stud 119 mounted in hole 119a of lever 83 and to stationary spring hinge 1 20 fixed to frame 80, the action of this spring 118 being such that all joints and levers, are controlled by a constant tension so that levers 78 and 83 are Constantly applying pressure to stems 76 and 82 at points 79 and 84. Spring 118 resists outward movement of stems 76 and 82 caused by rising temperatures and causes the entire described linkage system to follow stems 76 and 82 as they retract under the influence of lowering temperatures. In addition, tension spring 121, fixed to lever 65 at aperture 121a and to stud 123.11 fixed to housing 10, provides a constant bias on lever 65, urging it in the same direction as spring 118 to take up any looseness in the pivotal mountings of lever 65.

As heretofore related, the various fluids have ditfering rates of expansion per degree of temperature change. Therefore, I have provided means whereby the change of ratio caused by movement of friction roller 39 on platform gear 37 can be lesser or greater in response to a fixed increment of movement of stem 76.

Carrier 109, adjustable in a line at right angles to a line passing through the centers of studs 81 and 86 and through studs 111 and 112, determines the position of cross slide 97, which, in turn, positions studs 89 and 96 lengthwise in slots 87 and 88 of levers 78 and 83 and in lever arm relationship, to studs 81 and 86, thus changing the ratio of movement between point 79, pivot 81 and stud 89 as well as between point 84, pivot 86 and stud 96, and thus changing the lateral response of studs 89, 96, slide 103, cross slide 97 and stud 113.

Also, as carrier 109 is moved, stud 113 is caused to move lengthwise in slot 114 of lever 65 which varies the lever arm ratio between 116, stud 113 and point 65a and thus varies the response of slide 58 and roller 39 to a fixed movement of stem 76.

Carrier 109 is positioned by manually operated screw 1 22. Pointer 123 is visually aligned with an appropriate scale 124 mounted in the case of the temperature compensator. Scale 124, is provided with slots 125 and 1.26, which permit this scale to be adjusted empirically to secure the correct response on the. linkage described.

Bellows 77 has an adjusting screw (not shown attached in fixed relationship thereto so that the entire bsll w s b y n. be ms ax a lyb urni fn t 12. 0 h and 2 e i s ns c e A 911. .,1 in he flan 2 b lc qqp r s h. P n v x to: they frame. 10 looks the, bellows 77 against rotating on its axis. during adjustment. The entire device can be calibrated by setting carrier 109 at a predetermined position, immersing bulb 72 in a liquid held at exactly 60 F. temperature. and adjusting nut 128 and position of bellows. 77.- and; stem 82 until the exact required input to output ratio; of 1:1 is obtained.

The total temperature. range for any. coefiicient of expansion of metered liquid is determined by the formula ea h, ee. of:

temperature change in bulb 72 the stem 76 moves; .00125 of an inch with a total available travel from this source of .250. The actuating lever 65 has a lengthof. 9.6667 inches from the center of stud 64 to the center of stud 117, and the lever 78 has a length of .7286 fromthe center of stem 76 to the center of pivot stud 81. The pivot stud is 1.8536 inches from the center line of the friction roller 39. The tabulated figures given in Table I represent: T=total allowable temperature change in degrees Fahrenheit, R=total allowable platform setting in inches, B=total travel of stem 76 in inches, K=,cofii ient Q pansion of iq d being e ed, %=tota1 percent of change of speed ratio from input to output within the range of this device, and L is the distance from the center of stud 64 to stud 113 in inches.

Table No. 1

K T R B L .0003 400 .375 500 2. 3873 12 70001 300 .375 375 2. 5229 12 .0005 210 375 300 2. 6433 12 .0000 200 375 250 2. 7508 12 .0007 171. 43 375 2142 2. 8178 12 .0008 150 .375 1875 2. 93 .0 12 .0009 133. 3 .375 1006 3. 01 109 12 .0010 120 375 150 3. 0867 12 .0011 109. 03 .375 1366 3. 1519 12 .0012 100 .375 125 3. 2141 12 .0013 9228 .375 1151 3. 2703 12 .0011 85.7 .375 1072 3. 3220 12 .0015 so .375 .100 a 3703 12 0010 75 .375 .0030 3. 41536 12 .0017 70, 53 .375 .0882 3. 4570s 12 .0018 60. 60 .375 .0833 3 4070 12 Thus, with a manual adjustment of screw 122, the distance L may be varied to obtain a setting corresponding to the coefiicient of expansion of the liquid being metered, and the input to output speed ratio will then, automatically be adjusted for changes in the temperature of the liquid within the range of temperature in column T, to provide a correction to 60 F.

Figs. 6-9 illustrate the combined operation of the bellows 74 and 77 and their cooperating linkage and their eiTec-t on the friction roller 39.

Fig. 6 illustrates both bellows at a mean position, in which case all of the linkage assumes a mean position, as does the friction roller 39 on platform gear 37. The carrier 109 is set at a coefiicient of .0018, and thus the studs 89 and 96 lie in a line parallel to and furtherest from shaft 41 and consequently the line of travel of friction roller 39.

Fig. 7 illustrates the eflect of a minus change in am: bient temperature. Both bellows 74 and 77 contract moving stems 76 and 82 outwardly in opposite directions and in equal'distances. has beendescribed, the toggle system 'cancels out the effect of this; equal movement of the stern and the mean position of lever 65v and,

correspondingly, the mean position of the friction roller 39 on platform gear 37 remains unchanged. Carrier 109 is still set at a coefficient of .0018.

Fig. 8 illustrates bellows 77 and stem 82at a mean position, as in Fig. 6, but bellows 74 is now affected by a minus change in temperature sensed by bulb 72, and, as a consequence, stem 76 moves outwarddly. The lever 78 moves in a counterclockwise direction, forcingstud 89 to the right. Stud 96 is held fixed and thus the studs 106, 108, 101 and 113 move to the right, pivoting the lever 65' clockwise to accomplish a change in position of friction roller 39 on platform gear 37 to provide a compensating change in input to output ratio. Carrier 109 is setat a coeflicient of .0018.

Fig. 9 illustrates bellows 77 and stem 82 at a mean position as in Fig. 6, but bellows 74 is now affected by aplus change. in temperature in bulb 72, and as a consequencethe linkagehas moved laterally and oppositely to. that-illustrated in Pig. 8.1208060mp11511 a change ii -post;

- 9 tion of friction roller 39 on platform gear 37 to provide a compensating change in input to output ratio. Carrier 109 is illustrated as having been set at a coefiicient of .0003, so that studs 89 and 96 lie in a line parallel to and closest to shaft 41.

It is to be understood that the form of my invention, herewith shown and described, is to be taken as a preferred example of the same, and that various changes in the shape, size, and arrangement of parts may be resorted to, without departing from the spirit of my invention, or the scope of the attached claims.

Having thus described my invention, what I claim and desire to secure by Letters Patent is:

1. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, asecond fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a quadrilateral linkage assembly pivotally connected at each corner thereof, said linkage including movable opposite first and second corners and movable opposite third and fourth corners, means connecting said linkage assembly to said lever to move said actuating lever in response to movement of said first and second corners of said linkage assembly, a second lever pivotally mounted intermediate its end on said second fixed pivot and having one end pivotally connected to said third corner of said linkage assembly, a third lever pivotally mounted intermediate its ends on said third fixed pivot and having one end pivotally connected to said fourth corner of said linkage assembly, a first condition responsive means adapted to move the other end of said.

second lever, and a second condition responsive means adapted to move the other end of said third lever ina direction generally opposite to the movement of said second lever, whereby said actuating lever is moved proportionally to the difference in movement of said other ends of said second and third levers.

2. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a quadrilateral linkage assembly pivotally connected at each corner thereof, said linkage including movable opposite first andseco-nd corners and movable opposite third and fourth corners, means connecting said linkage assembly to said lever to move said actuating lever in response to movement of said first and second corners of said linkage assembly, a second lever' pivotally mounted intermediate its ends on said second fixed pivot and having one end pivotally connected to said third corner of said linkage assembly, a third lever pivotally mounted intermediate its ends on said third fixed pivot and having one end pivotally connected to said fourth corner of said linkage assembly, a first condition responsive means adapted to move the other end of said second lever, a second condition responsive means adapted to move the other end of said third lever in a direction generally opposite to the movement of said second lever, whereby said actuating lever is moved proportionally to the difference in movement of said other ends of said second and third levers, and spring means to bias said second lever in a direction opposite to the force exerted thereon by said first condition responsive means.

3. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a second lever pivotally connected intermediate its ends on said second fixed pivot, said second lever having formed therethrough at one end a longitudinal slot, a third lever pivotally mounted intermediate its ends on said third fixed pivot, said third lever 10 having formed therethrough at one end a longitudinal slot; a quadrilateral linkage assembly pivotally connected at each of its four corners and having first, second, third and fourth studs mounted at respective corners thereof,

fixed pivots and adapted to be moved in a direction nor-' mal to a line between said second and third fixed pivots, said cross link having formed therethrough a plurality of longitudinal slots slidably receiving said third and fourth studs of said assembly; a first condition responsive means adapted to move the other end of said second lever, and a second condition responsive means adapted'to move the other end of said third lever in a direction opposite to the movement of said second lever; whereby the actuating lever is moved proportionally to the difference in movement of said other ends of said second and third levers, and whereby the proportionality of such actuating lever movement is governed by the spacing of said cross link from said second and third fixed pivots.

4. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a second lever pivotally connected intermediate its ends on said second fixed pivot, said second lever having formed therethrough at one end a longitudinal slot, a third lever pivotally mounted intermediate its ends on said third fixed pivot, said third lever having formed therethrough at one end a longitudinal slot; a quadrilateral linkage assembly pivotally connected at each of its four corners and having first, second, third and fourth studs mounted at respective corners thereof, said first and second studs being mounted at opposite corners of said linkage assembly, said third stud being slidably received in said second lever slot and said fourth stud being slidably received in said third lever slot; means connecting said linkage assembly to said actuating lever to move said lever in response to the movement of said first and second studs. said meansiricluding a cross link mounted on said frame parallel to said second and third fixed pivots and adapted to be oved in a direction normal to a line betwem said second and third fixed pivots, said cross link having formed therethrough a plurality of longitudinal slots slidably receiving said third and fourth studs of said assembly; a first condition responsive means adapted to move the other end of said second lever, and a second condition responsive means adapted to move the other end of said third lever in a direction opposite to the movement of said second lever; whereby the actuating lever is moved proportionally to the difference in movement of said other ends of said second and third levers, and whereby the proportionality of such actuating lever movement is governed by the spacing of said cross link from said second and third fixed pivots; and spring bias means to bias said actuating lever in a direction opposite to the force exerted thereon by said first condition responsive means.

5. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a second lever pivotally connected intermediate its ends on said second fixed pivot, said second lever having formed therethrough at one end a longitudinal slot, a third lever pivotally mount ed intermediate its ends on said third fixed pivot, said' third lever having formed therethrough at one end a Longitudinal slot; a quadrilateral linkage assembly pivotally connected at each of its four corners and having first, second, third and fourth studs mounted at respective corners thereof, said first and second studs being mounted at opposite corners of said linkage assembly, said third and fourth studs being slidably received respectively in saidsecond lever slot and said third lever slot; means connecting said linkage assembly to said actuating lever to move said lever in response to the movement of said first and second studs, said means including a slide, bar, having a pivot opening at one'end and a slotted opening atthe other end, said pivot and slotted openings respectively receiving said first and second studs; a first condition responsive means adapted to move the other end of said second lever, and a secondcondition responsive means adapted to move the other end of said third lever in a direction opposite to the movement of said second lever; whereby the actuating lever is moved proportionally to the difference in movement of said other ends of said second and third levers.

6.. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating lever pivotally mounted on said first fixed pivot, said lever having an elongated slot opening therethrough, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame onthe other side of said actuating lever, a second lever pivotally connected intermediate its ends on said second fixed pivot, said second lever having formed therethrough at one end a longitudinal slot, at third lever pivotally mounted intermediate its ends on said third fixed pivot, said third lever having formed therethrough at one end a longitudinal slot; a quadrilateral linkage assembly pivotal- 1y connected at each of its four corners and havingfirst, second, third and fourth studs mounted at respective corners thereof, said first and second studs being mounted at opposite corners of said linkage assembly, said third and fourth studs being slidably received respectively in said second lever slot and said third lever slot; means connecting said linkage assembly to said actuating lever to move said lever in response to the movement, of said first and second studs, said means comprising a slide bar having a pivot opening at one end, a first slotted opening at the other end and a second slotted opening therebetween, said end openings respectively receiving said first and second studs, and a cross link mounted on saidv frame parallel to said second and third fixed pivots: and adapted to be moved in a direction normal to a line between said second and third fixed pivots, said cross link having a longitudinal slot at each end and a projecting stud therebetween, said end slots respectively receiving said third and fourth studs of said assembly and said projecting stud engaged with said second slotted opening of said slide bar and said elongated slot opening of said actuating lever; whereby the actuating lever is moved proportionally to the diiference in movement of said other ends of said second and third levers, and whereby the proportionality of such actuating lever movement is governed by the spacing of said cross link from said second and third fixed pivots.

7. In an automatic temperature compensator, a frame having a first fixed pivot, an actuating, lever pivotally mounted on said first fixed pivot, a second fixed pivot mounted on said frame on one side of said actuating lever, a third fixed pivot mounted on said frame on the other side of said actuating lever, a quadrilateral linkage assembly pivotally connected at each corner thereof, said linkage including movable opposite first and second corners and movable opposite third and fourth corners, studs on said linkage, assembly at said first and second corners thereof, means connecting said linkage assembly to said lever to move said actuating lever in response to movement of said studs, a second lever. pivotally mounted intermediate its ends on said second fixed pivot and having one end pivotally connected to said third corner of said linkage assembly, a third'lever pivotally mounted intermediate its ends on said third fixed pivot and having one end pivotally connected to said fourth corner of said linkage assembly, whereby said actuating lever is moved proportionally tothe difference in movement of said third and fourth corners by operation of said second and thirdlevers.

References Cited in the file of this patent UNITED STATES PATENTS 1,190,215 Becker July 4, 1916 2,193,095 Harrison Mar. 12, 1940 2,341,741 Putnam Feb. 15, 1944 2,549,653 Wilson Apr. 17, 1951 2,661,012 Militano Dec. 1, 1953 2,680,970, Durkee June15, 1954 

